Lubricant feeding system for shaft and hub profile assemblies with axial longitudinal displacement capacity

ABSTRACT

A lubricant feeding system for shaft and hub profile assemblies that can move longitudinally along an axis. A first exterior assembly member (e.g., shaft or hub) encloses at least partly a second interior member (e.g., hub or shaft) along the circumference. At least one distributing channel, extending circumferentially over at least part of the inner circumference, is provided in the region of the profile base. This distributing channel is coupled with at least one lubricant feeding channel extending towards the external circumference of the assembly exterior member The invention includes a distributing member extending circumferentially over the length of the distributing channel, splits the distributing channel into a first partial area located radially outward and a second partial area located radially inward. The distributing member and the distributing channel are designed to form, when they co-operate, a plurality of valve areas between the first and the second partial of the distributing channel.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The invention is relative to a lubricant supply system for profileconnections such as unions, assemblies, and linkages of shaft and hubwith the ability to move axially and longitudinally, specifically withthe features of the generic part of claim 1.

2. Description of the Related Art

Positive form-locking connections for transferring torque in the form ofprofile connections which additionally permit the possibility of arelative movement of shaft and hub in the axial direction are known in aplurality of designs for various applications. Voith publication G 1 1214.85 discloses a compact drive shaft with axial, longitudinalcompensation in the middle area in the form of a profile connection. Astop is associated with the axial, longitudinal compensation forlimiting the axial movement. In order to assure the realization of theoperation and to keep down wear, it is necessary that the profileconnection be lubricated over the entire width to a sufficient degree.It is customary to associate appropriate lubricating devices with thehub parts of the profile connection, which lubricating devices arecoupled to a lubricant supply conduit in a profile groove worked intothe inner circumference of the hub part. The profile groove runs in thecircumferential direction of the hub part, that is, in the direction ofrotation or counter to the direction of rotation. The lubricant shouldthen be distributed essentially in the distributor groove arranged onthe inner circumference of the hub part and pass into the space realizedby the groove worked into the projecting profiles and consequentlyforming an intermediate space which cannot be bridged. The lubricationagain passes into the intermediate spaces between the profile parts ofshaft and hub contacting each other (recesses and projections), whichintermediate spaces are conditioned by the play existing during themeshing of the is profiles of the individual components of the profileconnections, so that the lubricant can be distributed essentially overthe entire axial extent of the profile connection.

However, such a design has the significant disadvantage that in the caseof profile connections with a large diameter, in order to assure asufficient supply of lubricant, a correspondingly great amount oflubricant is required. In order to bring in the large amounts oflubricant into the distributor groove and distribute it over the axialextent of the profile connection and/or the entire extent in axialdirection of the individual components of the profile connection uponaxial and longitudinal movement, a certain time is required for thiswhich, results in standstill times in work machines driven by a drivetrain with integrated profile connection.

Another significant disadvantage is the fact that in order to realize alubrication which is as uniform and complete as possible, which requiresa large amount of lubricant, an increasing contamination of the systemmust be accepted at the same time. The operating unit has no influenceon the lubrication itself except in the immediate area of thearrangement of the lubricant supply conduits. Thus, there is thepossibility that in spite of an elevated pressure of lubricant, sincethe excess lubricant exits out of the profile connection upon axial,longitudinal movement, no complete lubrication is performed.

The invention is therefore based on the problem of further developing aprofile connection with the ability to move axially and longitudinallyof the initially cited type in such a manner that the citeddisadvantages are avoided. In particular, the required amount oflubricant should be significantly reduced and the required timeintervals between the individual lubricant supply cycles should also bemade longer. Moreover, the lubricant supply system should bedistinguished by a simple design to realize as complete and uniform alubrication as possible of the individual components of the profileconnection of shaft and hub. The lubrication should take place in anobligatory manner and not be a function of the number of lubricantsupply conduits connecting the outer circumference of the hub to thedistributor groove.

SUMMARY OF THE INVENTION

The lubricant supply system for a profile connection of a shaft and of ahub with the ability to shift axially and longitudinally, the systemincluding a first outer element of the profile connection, shaft or hub,which surrounds another, second, inner element of the profileconnection, hub or shaft, at least partially in the circumferentialdirection comprises either at least a distributor groove arranged in thearea of the profile base on the circumference of the outer element ofthe profile connection and extending through the profile projections, ora distributor groove arranged in the area of the profile base on theouter circumference of the inner element of the profile connection andextending through the profile projections.

The distributor groove extends in the first instance over at least apart of the inner circumference of the outer element of the profileconnection in the circumferential direction and is coupled to at leastone lubricant supply conduit extending to the outer circumference of theouter element of the profile connection. In the second instance thedistributor groove extends over at least a part of the outercircumference of the inner element of the profile connection in thecircumferential direction and is coupled to at least one lubricantsupply conduit extending to the axis of symmetry of the inner element.

According to the invention a distributor element is arranged extendingin the shaft over its length in the circumferential direction. Thedistributor element divides the distributor groove into a first partialarea located radially outside and into a second partial area locatedradially inside. The distributor element and the distributor groove areshaped and designed in such a manner that they form in their cooperationat least one, but preferably a plurality of valve positions between thefirst and the second partial area of the distributor groove. Either theshaft or the hub function as an outer element of the profile connectiondepending on the association with the drive end or with the output end.

This valve action achieves at first a distribution of the amount oflubricant on the outer circumference or the inner circumference of thedistributor element via the distributor groove before the lubricantpasses over to the second partial area and passes therewith into atleast profile gaps occasioned by the working in of the distributorgroove in the profile projections of the outer element or of the innerelement of the profile connection and into the areas coupled to thelatter, which areas are occasioned by the profiles of the individualelements of the profile connection which profiles mesh with each other.This can assure an almost uniform supply of lubricant which can bedetermined in time over the entire circumference or at least the partialarea of the profile cross section which the distributor groovesurrounds. In addition, the solution in accordance with the inventionmakes it possible to lubricate profile connections, especially profileconnections with a large diameter or areas of profile cross sectionswith a large surface as uniformly and completely as possible with aprecisely dosed amount of lubricant. That means that only the amount oflubricant is always used which is actually required and thuscontamination, which increases with the amount of lubricant used, can beavoided for the system. In particular, such a device can be retrofittedwithout great problems into systems which already exist and are in use,since as a rule a central distributor groove is already present and nogreat expense for retrofitting and working is required for realizing thevalve function given the appropriate designing and the use of suitabledistributor elements, preferably annular elements.

The two basic variants cited in the following are conceivable for theassociation and design of the distributor groove in the circumferentialdirection.

1. At least one distributor groove covering only a partial area in thecircumferential direction or a plurality of these grooves arranged inseries in the circumferential direction is/are provided. The distributorgrooves are free of a coupling among themselves.

2. The distributor groove extends over the entire circumference relativeto the cross section of the outer element or, in the second instance ofthe inner element, preferably annularly in the circumferentialdirection, that is, over the entire inner circumference of the outerelement of the profile connection or over the entire outer circumferenceof the inner element. The distributor element is designed in thisinstance as an annular element, preferably as a closed annular element.

The first possibility offers the advantage that even critical areas of ashaft-hub profile connection can be lubricated separately by themselvesand/or in a reinforced manner without the lubrication having to takeplace over the entire circumferential area. The arrangement of thedistributor grooves to each other in the circumferential directionpreferably takes place in such a manner that the individual distributorgrooves are separated from each other only by a profile projection onthe outer element or, in the case of an arrangement on the innerelement, by a profile projection on the inner element of the profileconnection. Greater intervals between the individual distributor groovesare also conceivable.

In the case of the second, especially advantageous possibility thelubricant supply system for profile connections of shaft and hub withthe ability to move axially and longitudinally comprises for thefirst-mentioned instance of the arrangement of the distributor groove onthe outer element a distributor groove running in the area of the innercircumference of the outer element of the profile connection, e.g., ofthe hub, in the circumferential direction. The distributor groove can becoupled to a lubricant supply source via at least one lubricant supplyconduit which extends in radial direction to the outer circumference ofthe outer element of the profile connection, in this instance of thehub. The invention provides that a distributor element in the form of anannular element running in the circumferential direction and preferablyclosed in itself is arranged in the distributor groove. This annularelement divides the distributor groove into a first partial area and asecond partial area. The first partial area is provided, relative to theaxes of symmetry of shaft and hub in the assembled state, on a diameterwhich is greater than the diameter on which the second element isarranged. According to the invention the annular element exercises avalve action for the lubricant. That means that the lubricant can beintroduced into the second partial area, dosed in time and amount, fromwhich it runs into the profile connection. This design offers theadditional advantage that in the case of existing profile connectionsthe distributor grooves which are already present can be utilized andcan be readily retrofitted by providing the distributor ring as regardsthe functions to be achieved with the solution of the invention.

In the case of the second, especially advantageous possibility thelubricant supply system for profile connections of shaft and hub withthe ability to move axially and longitudinally comprises for thesecond-mentioned instance of the arrangement of the distributor grooveon the inner element a distributor groove running in the area of theouter circumference of the inner element of the profile connection inthe circumferential direction. The distributor groove can be coupled toa lubricant supply source via at least one lubricant supply conduitwhich extends in radial direction to the axis of symmetry of the innerelement of the profile connection. A central supply line through theinner element, which runs in the area of the axis of symmetry of theinner element through the latter, can be used as lubricant supplysource. The invention provides that a distributor element in the form ofan annular element running in the circumferential direction andpreferably closed in itself is arranged in the distributor groove. Thisannular element divides the distributor groove into a first partial areaand a second partial area. The first partial area is arranged, relativeto the axes of symmetry of shaft and hub in the assembled state, on adiameter which is smaller than the diameter on which the second partialarea is arranged. The annular element exercises a valve action for thelubricant. That means that in this instance too, the lubricant can beintroduced dosed in time and in amount from the first partial area intothe second partial area, from which it runs into the profile connection.

Grease is used with preference as lubricant. However, the use of oils orother lubricants is also conceivable.

The realization for both basic variants can occur in different manners.In particular, essentially two basic design variants are distinguished.

1. Sealing function of the distributor element or annular element, whichcan be canceled at least in the case of lubricant: supply in the area ofthe intermediate space following the distributor groove in the area ofthe profile of the outer element of the profile connection.

2. The provision of slots in the area of the bearing surfaces of thedistributor element or annular element in the distributor groove byproviding either appropriate recesses in the area of the distributorgroove and/or, however, appropriate recesses on the annular element.

The throttle effect can be adjusted via the ratio of the sum of thecross sections of the transfer slots to the sum of the cross sections ofthe distributor conduits, that is, among other things as a function ofthe number of distributor conduits and/or of their size. There is alsothe theoretical possibility of working throttle positions into thedistributor conduits or the distributor grooves and/or in the area ofthe transfer slots. The working in can also take place additionally tothe other measures.

In order to realize this design variant the distributor element or theannular element is to be selected, designed and arranged appropriatelywith regard to the material.

In the first-cited instance with the arrangement of the distributorgroove on the outer element the distributor element or the annularelement is designed in such a manner that it essentially seals thesecond partial area from the first partial area in the state of nosupplying of lubricant and in the state of the supplying of lubricant itpartially bends, under the building up of an overpressure in thedistributor conduit, at least in the area of the intermediate spaceswhich result on the projecting profile parts from the working in of thedistributor groove into the profile of the outer element of the profileconnection, e.g., of the hub and which are preferably designed to belarger in cross section than the cross section of the distributor grooveand as a result of the bending it delivers lubricant into thisintermediate space in order to remove the pressure, from which it passesinto the intermediate spaces of the intermeshing profiles.

The distributor element or the annular element then produces so-calledtransfer slots in these areas which slots are distinguished by ansignificantly smaller opening cross section than that of the lubricantsupply conduit. According to the invention a high pressure builds upthereby in the first partial area of the distributor groove during thesupplying of lubricant which pressure becomes active on the outersurface of the distributor element or of the annular element. As long asthe force conditioned by the pressure on the outer surface is less thanthe force directed in the opposing direction by the nature of thedistributor element or of the annular element or is in an equilibriumwith the latter force, the lubricant is forced to distribute itself inthe first partial area along the outer circumference of the distributorelement or of the annular element in the distributor groove. A bendingof the distributor element or of the annular element is not possible inthe area of the intermediate spaces in the projecting profiles until theforce exceeds the counterforce which can be generated by the distributorelement or the annular element. This bending produces a transfer slotbetween the first and the second partial area which makes possible aflow of lubricant from the first into the second partial area andtherewith a release of pressure in the first partial area. The slotbeing produced also exercises a dosing action at the same time thereby.However, these statements only apply in a modified fashion for theinstance of the first lubrication. During the first lubrication, thatis, before any lubricant at all is introduced into the distributorgroove, the distributor groove contains air with a low viscosity. Theair in the distributor groove must consequently first exit out of thegroove. In order to realize this it is sufficient to provide appropriatedifferences in roughness, e.g., in the area of the contact areas ofsealing element and wall of the distributor groove which differencesmake a transfer of air possible but still fulfil a sealing actionagainst lubricant. The pressure in the first partial area of thedistributor groove does not build up until after the escape of the air.The principle described here also applies in analogous fashion to thearrangement of the distributor groove on the inner element.

Another possibility then consists in designing the annular elementindependently of the arrangement of the distributor groove as amultipartite assembly, during which the sealing action and theproduction of the slots by the cooperation of the individual partelements are realized. A first possibility then consists in designingthe distributor element from a plurality of partial rings which arecoupled to each other yet can move against each other in axialdirection. Another possibility then consists in designing thedistributor element as a combination of a support ring and of a sealingring. The support ring is arranged inwardly in radial direction andsupports the sealing ring, which is arranged radially outward. Thesealing ring is then either deformed in radial direction under theaction of pressure in the first partial area of the distributor grooveand thus frees the corresponding slots by corresponding co-deformationof the support ring, or the sealing ring is provided with passages inthe direction of the support ring. In the last-cited instance thedesired passage slots can already be realized by providingcorresponding, appropriate surface rough areas on the outer side of thesupport ring facing the sealing ring and/or on the inside of the sealingelement facing the support ring and by the action of pressure.

The second possible basic variant consists in providing a distributorelement or an annular element in the distributor groove. In order toproduce the communication between the first and the second partial areaof the distributor groove pocket-like recesses are provided in the outerelement of the profile connection, e.g., the hub, in the area of theintermediate space conditioned by the groove on the individual profileprojections and/or corresponding, appropriate passages are provided onthe distributor element or on the annular element itself. The lattermake possible a throttling action during the transfer of the lubricantfrom the first partial area into the second partial area via thecorresponding opening cross sections. In this instance no complete sealis produced between the first and the second partial area in theoperating state of not filling with lubricant; however, the transfercross sections with a small diameter bring about a correspondingthrottling action so that the lubricant must be also distributed for themost part over at least a partial area of the circumference first, for apressure buildup, before a transfer takes place.

The solution in accordance with the invention makes it possible tolubricate large-diameter profile connections completely with a preciselydosed amount of lubricant with a distributor groove. That is, only theamount of lubricant is necessary which is actually needed. An additionalcontamination of the system, which increases with the amount oflubricant used, can be avoided. In particular, such a device can beretrofitted without great problems into already existing systems since acentral distributor groove is as a rule already present and, given theappropriate design and use of suitable annular elements, no greatexpense for reworking is necessary.

A great number of designs can be considered for the distributor element.For example, an annular element in the form of a piston support ring orof a partial area of a piston support ring is conceivable. Furtherpossibilities consist in the use of a strip of sheeting or of asemifinished material, of an elastomer, a glass-fiber carbon fiber tube,corrugated steel bands, etc. The distributor element or the annularelement can be designed from one layer or a plurality of layers whichform a construction unit with each other but can be moved or deformedagainst each other in axial direction. The individual layers, on theother hand, can be formed from a plurality of plies connected to eachother in an inseparable manner. This possibility is utilized inparticular for the designing of piston support rings in order to achievethe optimum qualities regarding elasticity and rigidity as well asresistance to wear. The plies forming the surfaces in thecircumferential direction are preferably made of especiallywear-resistant material. A further possibility resides in the designingof the distributor element as an assembly comprising at least onesupport element and one sealing element, as already explained above. Inthis instance too, the design and selection of the combination mostsuitable for use is a matter of the judgement of the responsible expertin the art.

When a distributor element or an annular element comprising severallayers is used, in particular, multilayer bands, e.g., in the form ofsteel bands or semifinished material are used. Other embodiments arealso conceivable.

The ends of the individual layers or of a distributor element in theform of an annular element can be designed either in the form of anoblique step, which is realized in particular when using annularelements in the form of a snap ring or circlip, or in the case ofelements subjected regarding their form of a high degree of rigidity. Inthe case of other layer embodiments it is furthermore conceivable toconnect the ends to each other in an overlapping manner, e.g., byadhesion, in which case the overlapping width is preferably filled outin correspondence with the width of the distributor groove. A furtherpossibility is to couple the ends so that they butt against each other.

The use of piston support rings in order to realize this function hasthe advantage that commercially available, standardized, annularelements can be used. So-called guide rings can also be used whichconsist of composite fabric materials and are used in highly stressedsliding connections. The latter exhibit as a rule a great resistance topressure and extraordinary wearing qualities which assure a long servicelife.

In sum, it can be established that the individual functions aredetermined by the form of the distributor element and/or its partialcomponents and/or the design of the distributor element and/or itspartial components and/or the selection of material and/or the surfacequality and/or the providing of passages.

A further significant advantage of the solution in accordance with theinvention is the fact that the system can be kept essentially free ofcontamination by means of the precise dosing via at least one, butpreferably several valve positions produced over the annular element inthe distributor groove.

Essentially two basic possibilities can be conceived for the design ofthe distributor groove:

1. The design of a distributor groove with essentially the same crosssection, viewed in radial direction.

2. The design of a distributor groove in radial direction with at leasttwo partial grooves of different dimensions in cross section.

In the case of the first-cited possibility it is necessary that thedistributor element or the annular element is provided for realizing thefunction of sealing action essentially with an appropriate widthtolerance so that this element rests with its side surfaces essentiallyon the inner surfaces of the distributor groove and only by the bendingdue to the high pressure in the first partial area can a correspondingslot be produced.

In the case of a division into two partial grooves and the arrangementof the distributor groove on the outer element the groove which is theouter one in the radial direction is provided with a smaller crosssection than the groove which is the inside one in the radial direction.In the case in which the distributor groove is arranged in the innerelement the groove which is the outer one in the radial direction has alarger cross section than the partial groove which is the inner one inthe radial direction. The cross-sectional transition is used as acontact or sealing surface, in which case a slot is also providedbetween the side areas and the inner surfaces of the distributor groove.This slot is significantly smaller in its cross section than the crosssection of the lubricant supply conduit associated with the distributorgroove. The seal is realized here essentially by the contacting of theannular element in the area of the distributor groove which is the innerone in the radial direction. In the case of loading with pressure and acorresponding bending of the annular element a transfer slot is producedby the lifting of the pressure ring in this area and can, as a result ofthe bending in the area of the teeth gaps, free a flowthrough crosssection to the latter.

For the case in which the slot seal is not sufficient, which can occurespecially in the case of large profiles, the annular element can dedesigned in such a manner that the width tolerances no longer has to bedetermined so precisely but rather can be made more generously in thatthe annular element is designed in the form of an O-ring seal. Thisconcerns a possibility of sealing which can be realized with standardcomponents and which can be defined. A support ring is associated withthe annular element is this instance, preferably for guidance. Thedivision into two partial areas in the distributor groove takes place inthis instance via the O-ring seal. The O-ring is shifted partially in aradial direction in the direction of the shaft due to elasticdeformation upon the loading with pressure when a correspondingly highpressure has been achieved. On the other hand, a bending is onlypossible in the area of the teeth gaps so that an exiting of lubricantfrom the first partial area of the distributor conduit into the teethcan take place only in these areas. The cross section of the supportring can be designed in different manners thereby. A rectangular form isconceivable, as is a rectangular form provided with a round area for abetter guidance of the O-ring. The precise selection is left to thejudgement of the expert in the art. The support ring itself is not onlyto be manufactured with the precise width tolerance required, but thearea at the ends of the support ring can be designed in a simpler mannersince this area no longer has any meaning for the sealing function.Another possibility in the case of the previously described variants ofminimizing as much as possible the influence of a connection of thesupport-ring ends on the method of operation consists in that in atleast bipartite designs of the distributor groove the connection isdesigned in such a manner that it extends in the radially outer area orinner area, depending on the association of the distributor groove tothe outer or the inner element, of the distributor groove. Thedistributor groove is preferably arranged in the circumferentialdirection of the profile connection. The distributor groove ispreferably worked completely into the profile base. The annular elementis preferably arranged in such a manner thereby that it seals with theprofile base essentially in the assembled state. However, anotherpossibility consists in designing the distributor groove, whenprojecting the vertical line to the line of symmetry of the hub into acommon plane, at an incline to the latter. This means that thedistributor groove does not have a cross section whose individualsurface components have the same axial interval relative to a referencesurface. In this instance the groove describes, when viewed from theright, a circular arc. In the other instance, given an inclined design,the groove describes an oval form upon the projection of this view intoone plane.

The solution of the invention can be used for a great number of profileconnections, e.g., for multi-groove profiles in the form ofsplined-shaft profile connections, for cogged or toothed profileconnections and for polygonal profile connections. The use in drive,i.e., cardan shafts with axial, longitudinal compensation is cited hereby was of example as a possible main area of application.

A great number of possibilities are also conceivable for the design ofthe distributor groove, ranging from a design with constant crosssection in radial direction to a design with a plurality ofcross-sectional modifications in radial direction with thecross-sectional dimensions increasing inwardly in radial direction, thatis, in the direction of the axis of symmetry of the hub. The transitionsare preferably designed to be rounded in order to prevent the notcheffect. It is pointed out once more by way of summation that the slotbeing produced or provided for the reaction of the valve effect has aconsiderably lesser cross-sectional dimension that the cross section ofthe infeed, especially of the lubricant supply conduit. Only theappropriate ratio between infeed and slot makes possible the pressurebuildup by a corresponding distribution of the lubricant on the outercircumference or inner circumference of the annular element as afunction of the distributor groove.

The annular element itself can have any desired cross section. However,embodiments with annular elements with rectangular or round crosssection are preferably used. However, other cross-sectional forms arealso not excluded.

The selection of the precise embodiment of the distributor groove and ofthe arrangement of the annular element as well as of its design asregards its shape, the cross section as well as of the material dependson the requirements of use, which are also, in particular, a function ofthe magnitude of the forces to be transferred and therewith of the sizeof the profile connection and are in the area of competency of theresponsible expert in the art.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-mentioned and other features and advantages of this invention,and the manner of attaining them, will become more apparent and theinvention will be better understood by reference to the followingdescription of an embodiment of the invention taken in conjunction withthe accompanying drawings, wherein:

FIGS. 1a and 1 b illustrate an embodiment of a lubricant supply designedin accordance with the invention and shown in an axial section and aview from the right;

FIGS. 2a and 2 b illustrate two possible embodiments of the courses ofdistributor grooves in the circumferential direction on the innercircumference of the hub;

FIG. 3 illustrates by way of example another embodiment of a design of alubricant system in accordance with the invention with a distributorgroove with constant cross section;

FIGS. 4a and 4 b illustrate two embodiments for the shaping of theconnection of the ends of the annular element;

FIG. 5 illustrates an embodiment of an annular element in the form of amulti-layer band;

FIGS. 6a to 6 c illustrate the embodiment of an annular element in theform of an O-ring seal with associated support ring in a distributorgroove with a different cross section as well as its method ofoperation;

FIG. 7 shows another embodiment of a lubricant supply system of aprofile connection, which system is designed in accordance with theinvention;

FIGS. 8a and 8 b illustrate other embodiments of the distributorelement; and

FIG. 9 illustrates an embodiment of a lubricant supply system, designedin accordance with the invention, of a profile connection in which thedistributor groove is arranged in the inner element of the profileconnection.

Corresponding reference characters indicate corresponding partsthroughout the several views. The exemplification set out hereinillustrates one preferred embodiment of the invention, in one form, andsuch exemplification is not to be construed as limiting the scope of theinvention in any manner.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1a illustrates in an axial section an advantageous embodiment of alubricant system 1 designed in accordance with the invention and for aprofile connection 2 of a shaft 3 and of a hub 4. Shaft 3 forms an innerelement of the profile connection here and hub 4 forms an outer elementof profile connection 2. Profile connection 2 is designed, in theinstance shown, as a splined-shaft connection.

Lubricant system 1 comprises distributor groove 6 running in the area ofinner circumference 5 of hub 4 in the circumferential direction of hub4. Distributor groove 6 is coupled to space 38 which is formed by theworking in of the groove into the profiles of the hub and which remainsuncovered even during the intermeshing of the profiles of shaft 3 and ofhub 4, and, is coupled above it to intermediate spaces 7 arising fromthe play of the individual profiles of the profile connection betweenshaft 3 and hub 4. Distributor groove 6 is worked into profile base 9 ofhub 4. The latter can be connected via at least one lubricant supplyconduit 8 to lubricant supply source 10 which can be coupled to thissupply conduit 8 and which is not shown in detail here.

Lubricant supply conduit 8 extends in radial direction from distributorgroove 6 to outer circumference 11 of hub 4. Lubricant supply conduit 8is preferably designed directly in radial direction, that is, verticallyto axis of symmetry S_(N) of hub 4. In this instance axis of symmetryS_(VK) of lubricant supply conduit 8 runs upon the projecting with axisof symmetry S_(N) into a common plane, vertically to the latter.However, an inclined design to a connection line between outercircumference 11 of the hub to its line of symmetry S_(N) is alsoconceivable. Distributor groove 6 is preferably arranged in analogydirectly in the circumferential direction of hub 4, that is, associatedwith a cross section which can be formed in the assembled state by aprofile section through hub 4 on a constant axial dimension from theside surfaces of hub 4 which preferably run parallel to each other. Thismeans that the middle line M_(VNopt) of distributor groove 6 runs uponprojection with axis of symmetry S_(N) of hub 4 into a common planevertically to the latter.

FIG. 2a illustrates a view I corresponding to FIG. 1a on inner surface 5of hub 4 in the folded-out state. The distributor groove is designatedwith 6.2 a.

However, it is also conceivable to arrange distributor groove 6 in thecircumferential direction inclined relative to optimal middle lineM_(VNopt) for the distributor groove. Such an embodiment is shown in aview onto inner surface 5 of hub 4 according to FIG. 2b. The middle lineof the distributor groove, designated here with 6.2 b, is designatedwith M_(VNG).

Distributor groove 6 worked into profile base 9 can be divided in theinstance shown into two partial distributor grooves, a first partialdistributor groove 6.1 which is also designated as the small distributorgroove and which is arranged in radial direction on a larger diameterd_(KV) than the second distributor groove 6.2, which is also designatedas the large distributor groove and is arranged on a smaller diameterd_(gV). The first distributor groove 6.1 has a smaller axial extension,that is, a smaller width b_(KV), than the second distributor groove 6.2with the width b_(gV). Annular element 12 is arranged in distributorgroove 6. This element serves to divide distributor groove 6 into twopartial areas 13, a first partial area 13.1 and a second partial area13.2. The first partial area 13.1 is arranged on a greater diameter,that is, viewed in radial direction, further outside than the secondpartial area 13.2. The first partial area 13.1 is therefore alsodesignated as the outer partial area whereas the second partial area13.2 can also be designated as inner partial area. The size of the firstpartial area 13.1 and its radial extension circumference is determinedin the concrete instance by the depth of small distributor groove 6.1 inradial direction. The second partial area 13.2, that is, the innerpartial area, is determined by the dimensions of the large distributorgroove 6.2, that is, of the second partial groove area with subtractionof cross-sectional area A of annular element 12.

Annular element 12, which forms in the normal state a closed innersurface 14 running essentially on a certain diameter d_(rE) and runningin the circumferential direction and surrounding, so to say, shaft 4 ona larger diameter, is preferably designed in such a manner that element12 seals first partial area 13.1 against the second partial area in astate in which no lubricant supply, that is, no new supply of lubricantis to take place. This is achieved by an appropriate fit between widthdimension b_(gV), the large distributor groove relative to the widthdimension b_(rE) of annular element 12. Another possibility, which canalso be realized by itself, consists in that only annular element 12rests in a partial area of its outer surface 15 on the transitionalsurface from small distributor groove 13.1 to large distributor groove13.2. The last-named embodiment takes place in particular if annularelement 12 has the appropriate rigidity which makes possible in any casea resting or contacting of at least one partial area of outer surface 15of annular element 12 in the assembled position. This is the case, as arule, if annular element 12 is introduced with oversize into distributorgroove 6, especially the large distributor groove 6.2.

During the supplying of lubricant by means of a lubricant supply source10 which can be connected to supply conduit 8 the lubricant passes intothe first partial area 13.1, in this instance small distributor groove6.1. The lubricant is distributed thereby in the circumferentialdirection of the annular element, during which a pressure is built up insmall distributor conduit 6.1 As long as there is no equilibrium betweenthis produced pressure and the counterforce produced by the rigidity ofannular element 12, that is, the pressure or the force exerted by thepressure on outer surface 15 is less or equal to the oppositely directedforce from annular element 12, no lubricant passes into largedistributor groove 13.2 When the pressure becomes greater in smalldistributor conduit 6.1 annular element 12 is readily deformed, e.g., inan elastic manner, and the sealing effect between annular element 12 andstop surface 16, that is, the first partial area 13.1 and the secondpartial area 13.2 is canceled. A small slot 17 or 18 then forms. Thisslot brings it about that the lubricant can exit from the first partialarea 13.1 to the second partial area 13.2 in a strongly dosed form. As aresult of the fact that the lubricant can not pass immediately fromsmall distributor groove 13.1 to large distributor groove 13.2 withoutflow resistance, it is forced to distribute itself in circumferentialdirection on outer surface 15 of annular element 12 at first until theappropriate elevated pressure is achieved.

Developing slot 17, regardless in which form, has a significantlysmaller cross section than lubricant supply cross section Q in supplyconduit 8. Annular element 12 is thus utilized to produce a resistancefor the lubricant in order to first force it to be distributed incircumferential direction in small distributor groove 6.1 and to permitan exit or transfer into large distributor groove 6.2 only aftercorresponding distribution in circumferential direction.

However, annular element 12 is preferably always designed with acorresponding width tolerance in regard to the width b_(gV) of largedistributor groove 6.2.

FIG. 1b illustrates a section corresponding to view II of FIG. 1a of thecross section of hub 4 in a state in which lubricant is being supplied.It is apparent therefrom how the form of the annular element is alteredin circumferential direction under the influence of pressure in thedistributor groove and therewith the lubricant from the first partialarea 13.1 into the second partial area 13.2 and therewith intointermediate spaces 7 which are determined by the play between theindividual profiles, especially the outer profile surfaces. Due to thefact that the lubricant is forced by the design of the invention beforethe transfer into intermediate space 7 to run over a part of outercircumference 15 of annular element 12, a single lubricant supplyconduit 8 can be sufficient already in the case of profile connectionswith a small diameter. In the case of profile connection with a ratherlarge diameter, like those used in particular in drive shafts withaxial, longitudinal compensation, preferably several lubricant supplyconduits 8 distributed over the circumference are arranged. The lattercan be arranged in different intervals from each other or distributed atequal intervals over the circumference.

Moreover, the cross-sectional transitions on the distributor grooves,especially small distributor groove 6.1 as well as large distributorgroove 6.2 are preferably designed to be rounded in order to reduce thenotch effect.

FIGS. 2a, 2 b illustrate the possibilities of the arrangement ofdistributor groove 6, shown here with 6.1 for the embodiment accordingto FIG. 1a and with 6.2 for an alternative embodiment in FIG. 2b. Thevariant which is the simplest and the most economical as regardsmanufacture consists in associating the distributor groove in thecircumferential direction with a certain cross section. This correspondsto the view onto inner circumference 5 according to FIG. 2a. FIG. 2billustrates an alternative embodiment; however care is to be taken herethat the lubricant path between annular element 12 and outer partialarea 13.1 of distributor groove 6 is enlarged compared to the design inFIG. 2a.

FIG. 3 illustrates a further alternative embodiment of the solution ofthe invention which is distinguished by simplicity and an economicalmanufacture. The basic structure corresponds to the solution accordingto FIG. 1a, for which reason the same reference numerals are used forthe same parts.

FIG. 3 illustrates a view in axial section onto profile connection 2.3comprising shaft 3.3 and hub 4.3. Distributor groove 6.3 is worked intoprofile base 9.3 which groove encompasses a constant cross section overits depth c3. Distributor groove 6.3 is associated with at least onelubricant supply conduit 8.3 which extends in the direction of outercircumference 11.3 of hub 4.3 and can be coupled as needed to lubricantsupply source 10. An annular element 12.3 is inserted with appropriatefit into annular distributor groove 6.3 and serves to form first partialarea 13.13 which is designated as outer partial area and a secondpartial area 13.23 designated as inner partial area. There are a greatnumber of possibilities for the designing and shaping of annular element12.3. In a first instance annular element 12.3 can be designed to berigid in axial direction, that is, over width b_(rE), but elastic inradial direction. This has the result that under loading with pressurethe ring experiences a bending over its width b_(rE) and as a resultforms a slot for the lubricant in the area of its side edges and incooperation with the inner walls of distributor groove 6.3, whichlubricant flows out of the first partial area 13.13 over into the secondpartial area 13.23. The size of the slot determines the amount offlowthrough.

Another possibility, which is not shown here, consists in providing anannular element in the form of a band in an embodiment corresponding toFIG. 1a which element can also be designed, e.g., in the form of anelastic band and achieves a sealing action by means of an appropriatefastening on the inner walls of the groove, on which fastening can alsotake place only partially; however, the areas of the teeth gaps, thatis, intermediate spaces 38 are held free from such a connection onaccount of the groove in the profile projections of hub 4.3.

FIGS. 4a, 4 b illustrate two possibilities for shaping the connection ofthe ends of annular element 12 in a view onto the cross section ofprofile connection 2.4 a and 2.4 b. FIG. 4a illustrates a connection inthe form of a junction or joint 20. The two ends butt on one anotherwith surfaces 21, 22 facing one another and are inseparably connected toone another by an adhesive or sealing compound. FIG. 4b shows anotherpossibility in the form of overlap 23 in which the two end areas 25, 26of annular element 12 come into abutment in the area of their outersurface 15 or inner surface 14. Overlap 23 is preferably provided in thearea of intermediate space 38 present on account of the working in ofgroove 6.3 into the profile projections of hub 4.4 in the form of atooth gap.

FIG. 5 illustrates another embodiment of an annular element in the formof a multilayer band 12.5. The individual layers are arranged superposedabove each other in radial direction and designated with 30 to 35. Thereis a sliding connection between the latter. The sliding connection makespossible a relative movement of individual layers 30 to 35 in axialdirection against each other. A sealing effect can be achieved by thedifferent positions in axial direction by means of this element 12.5and, upon loading with pressure, a release of a corresponding slot canbe achieved.

FIGS. 6a to 6 c illustrate a further embodiment of the distributorelement in the form of an annular element 12.6 comprising sealingelement 40 a and 40 b in the form of an O-ring and comprising a supportelement 36 a and 36 b. Sealing elements 40 a and 40 b in the form of anO-ring assume the division of distributor groove 6 into a first partialarea 13.16 and a second partial area 13.26. A third partial area 13.36is provided in the instance shown. Since O-ring 40 a and 40 b aredesigned to be relatively elastic, support ring 36 is associated with itfor guidance, which support ring is connected into the O-ringsubsequently in radial direction in the direction of the axis ofsymmetry of hub S_(N). Support ring 36 has the task in particular ofassuming guide tasks.

FIG. 6b illustrates an arrangement of an annular element 12.6 bcomprising sealing element 40 b and support element 36 b in accordancewith FIG. 6a in distributor groove 6.6 b with a cross section which isconstant in radial direction. FIG. 6c illustrates the associated methodof operation. It is apparent therefrom that due to the pressuredeveloping during the supplying of lubricant, O-ring 40 b experiences adeformation in the area of the profile gap on account of its elasticitywhich deformation makes possible a transfer of the lubricant in dosedform.

FIG. 7 illustrates by way of example and in a schematically simplifiedfashion an embodiment with several distributor grooves 6.71, 6.7 b.These grooves extend over a partial area of the circumference incircumferential direction, associated with a certain cross section ofhub 4.7 and arranged in series. The two distributor grooves 6.7 a and6.7 b are separated from one another by profile projection 41 a of hub4.7. Distributor elements 12.7 a and 12.7 b are arranged in distributorgrooves 6.71 and 6.7 b. The method of operation and the construction ofdistributor elements 12.7 a and 1/7 b can correspond to the embodimentsdescribed in FIGS. 1-6 and 8. The determination of the number and thelength of the distributor grooves, their shape and the selection of thedistributor elements as well as their shape is left to the expert in theart.

FIGS. 8a and 8 b illustrate in a section from an axial section anotherembodiment of a distributor element 12.8 in the form of a structuralcomponent comprising a support element 45 a and 45 b and a sealingelement 46 a and 46 b in a distributor groove 6.8 a and 6.8 b. Thedistributor groove has a constant cross section in the instance shown.However, a design with several cross sections with different dimensionsor in accordance with FIG. 1a or 6 a is also conceivable. In FIG. 8a thesealing action is achieved due to the slightly conical shaping ofsealing element 46 a, here due to the U-shaped cross section of sealingelement 46 a. However, a design corresponding to FIG. 8b is alsoconceivable in which design the sealing element is fitted with anappropriate fit, e.g. a transition fit or press fit, but preferably witha tight fit into distributor groove 6.8 b. Sealing elements 46 a and 46b have at least one through opening 47 a and 47 b extending from outercircumference 48 a and 48 b of sealing element 46 a, 46 b to innercircumference 49 a, 49 b of the sealing element. Support element 45 a,45 b and sealing element 46 a, 46 b make contact at least over a part oftheir outer surface 50 a, 50 b and/or their inner surface 49 a, 49 b,viewed in the assembled state. Outer surface 50 a, 50 b of support ring45 a, 45 b is provided with a certain roughness which is, e.g., greaterthan the roughness of inner surface 49 a, 49 b of sealing element 46 a,46 b. There is also the possibility of making the roughness of innersurface 49 a, 49 b of the sealing element greater than that of outersurface 50 a, 50 b of support element 45 a, 45 b or equal to it. Duringfilling with lubricant, the rough surface first allows the air to flowout with little resistance. If distributor groove 6.18 a, 6.18 b is fullof grease the contact point between the sealing element and the supportelement with its rough surface acts like a small leakage position. Theincreased resistance due to the high viscosity of grease allows thepressure in the distributor groove to rise. The leak can be enlarged orreduced with the size and/or the number of through openings.

FIG. 9 illustrates in axial section another advantageous embodiment of alubricant system 1.9 designed in accordance with the invention for aprofile connection 2.9 of a shaft 3.9 and a hub 4.9. Shaft 3.9 alsoforms an inner element of the profile connection and hub 4.9 an outerelement of profile connection 2. Profile connection 2.9 is designed as asplined-shaft connection. Lubricant system 1.9 comprises distributorgroove 6.9 running in the area of outer circumference 60 of shaft 3.9 inthe circumferential direction of the shaft. Distributor groove 6.9 iscoupled to area 61 which is formed due to the working in of thedistributor groove into the profiles of shaft 3.9 and which area remainsuncovered even during the intermeshing of the profiles of shaft 3.9 andhub 4.9 and is coupled over it to intermediate spaces 62 arising as aresult of the play of the individual profiles of profile connection 2.9between shaft 3.9 and hub 4.9. Distributor groove 6.9 is worked intoprofile base 63 of shaft 3.9. The latter can be coupled via at least onelubricant supply conduit 6.9 to lubricant supply source (not shown indetail here) which can be coupled to it. The coupling between lubricantsupply conduit 9.9 and lubricant supply source takes place via centrallubricant supply line 64 extending through the inner element, that is,shaft 3.9. Lubricant supply line 64 is arranged with preference in thearea of axis of symmetry S of inner element 3.9. However, embodimentsare also conceivable which comprise an arrangement of a plurality oflubricant supply lines 64 at uniform intervals in the circumferentialdirection on a certain diameter of the inner element in order not toproduce any imbalances caused by the lubricant supply system during theoperation of the drive shaft. In the instance shown, central lubricantsupply line 64 can be supplied with lubricant via lubricant line 65which can be coupled to it and which extends from central lubricantsupply line 64 in radial direction to outer circumference 66 of shaft3.9.

Distributor groove 6.9 worked into profile base 63 can be divided in theinstance shown into two distributor grooves, a first distributor groove6.1.9, which is also designated as small distributor groove and isarranged in radial direction on a smaller diameter d than the seconddistributor groove 6.2.9, which is also designated as large distributorgroove and is arranged on a larger diameter d than the first distributorgroove. The first distributor groove 6.1.9 has a lesser axial extent,that is, lesser width than the second distributor groove 6.2.9. Thedistributor element, which is designed as an annular element, isdesignated with 12.9 and arranged in distributor groove 6.9. It servesto divide distributor groove 6 into two partial areas 13.9, a firstpartial area 13.1.9 and a second partial area 13.2.9. The first partialarea 13.1.9 is arranged on a smaller diameter, viewed in radialdirection, than the second partial area 13.2.9. The first partial areais designated as inner partial area whereas the second partial area13.2.9 can also be designated as outer partial area. The extent of thefirst partial area 13.1.9 is determined in radial direction by the depthof the small distributor groove 6.1.9 minus the thickness of distributorelement 12.9. The second partial area 13.2.9, that is, the outer partialarea, is determined by the dimensions of the large distributor groove6.2.9 in radial direction. The method of operation of distributorelement 12.9 corresponds to that described in preceding FIGS. 1 to 8.Even the statements concerning the designing of distributor element12.9, especially the design in circumferential direction as well as inradial direction and the distributor groove as well as the coupling withadditional sealing elements apply by analogy to this embodimentaccording to FIG. 9.

In the embodiments according to FIGS. 1 to 9 the outer element of theprofile connection is designed, by way of example, as a hub. It is alsoconceivable to assign the operation of the shaft to the outer element ofthe profile connection.

While this invention has been described as having a preferred design,the present invention can be further modified within the spirit andscope of this disclosure. This application is therefore intended tocover any variations, uses, or adaptations of the invention using itsgeneral principles. Further, this application is intended to cover suchdepartures from the present disclosure as come within known or customarypractice in the art to which this invention pertains and which fallwithin the limits of the appended claims.

What is claimed is:
 1. A lubricant supply system for a profileconnection of a shaft and of a hub with the ability to transfer torquebetween said shaft and hub and move axially and longitudinally, saidsupply system comprising: a first outer element having an inner and anouter circumference, said element on a base of the profile connectionwhich surrounds another, second inner element of the profile connectionat least partially in a circumferential direction, said first outerelement attached to said hub and said second inner element attached tosaid shaft; at least one distributor groove extending in circumferentialdirection over at least a part of the inner circumference is arranged inthe area of the profile base on the inner circumference of the outerelement of the profile connection, said distributor groove locatedbetween said first outer element and said second inner element; at leastone lubrication supply conduit; said distributor groove coupled to saidat least one lubricant supply conduit which extend to the outercircumference of said outer element of the profile connection; adistributor element extending over the length of the distributor groovein circumferential direction and arranged in said distributor groovesaid distributor element dividing the distributor groove into a firstpartial area located radially outside and into a second partial arealocated radially inside; and said distributor element and saiddistributor groove constructed in such a manner that they form in theircooperation a plurality of valve positions between said first and saidsecond partial areas of said distributor groove.
 2. A lubricant supplysystem for a profile connection of a shaft and of a hub with the abilityto transfer torque between said shaft and hub and move axially andlongitudinally, said supply system comprising: a first outer element ona base of the profile connection surrounds another second, inner elementof the profile connection, at least partially in a circumferentialdirection said inner element having an outer circumference, said firstouter element attached to said hub and said second inner elementattached to said shaft; at least one distributor groove extending overat least a part of the outer circumference in circumferential directionis arranged in the area of the profile base on the outer circumferenceof said inner element of the profile connection; at least onelubrication supply conduit; said distributor groove coupled to said atleast one lubricant supply conduit extending through the inside of saidinner element of the profile connection; a distributor element extendingover the length of said distributor groove in circumferential directionand arranged in said distributor groove, said distributor elementdividing said distributor groove into a first partial area locatedradially outside and into a second partial area located radially inside;and said distributor element and said distributor groove constructed insuch a manner that they form in their cooperation a plurality of valvepositions between said first and said second partial area of thedistributor groove.
 3. The lubricant supply system according to claim 1,in which a plurality of distributor grooves are provided which extend incircumferential direction over at least a part of the circumference andare arranged in series in circumferential direction, said distributorgrooves are free of a coupling between one another.
 4. The lubricantsupply system according to claim 3, in which the individual saiddistributor grooves are arranged in series in circumferential directionare separated from one another only by a profile projection on saidouter element of the profile connection when the distributor grooves arearranged on said outer element.
 5. The lubricant supply system accordingto claim 1, in which said distributor groove extends in circumferentialdirection around the entire circumference; and said distributor elementis designed as an annular distributor element.
 6. The lubricant supplysystem according to claim 2, in which said distributor groove issymmetrically designed when arranged in said inner element of theprofile connection, observed in a view onto the cross section of saidinner element of the profile connection, with regard to a plurality ofaxes lying in the cross-sectional plane of said inner element of theprofile connection and extending through the axis of rotational symmetryof said distributor groove; and the axes of symmetry of the distributorgroove, which lie in the cross section of the outer circumference ofinner element of the profile connection run vertically to the axis ofrotational symmetry of the inner element.
 7. The lubricant supply systemaccording to claim 5, in which said distributor groove is symmetricallydesigned, observed when projecting a view onto its cross section into aplane with the cross section of the outer element of the profileconnection, and has an oval cross section.
 8. The lubricant supplysystem according to claim 1, said outer element having profileprojection and in which said second partial area also comprises at leasta part of a profile gap arising from the working in of said groove intoa profile projections on said outer element of the profile connectionwhen said distributor groove is arranged in said outer element, viewedin an axial section through the outer element of the profile connection.9. The lubricant supply system of claim 1, said outer element havingprofile projection and in which said second partial area of saiddistributor groove is coupled to one of intermediate spaces which areformed by profile gaps in the profile projections of said outer elementof the profile connection and by profile gaps in the profile projectionsof said inner element of the profile connection; and the width of theintermediate space is greater than the width of said second partialarea.
 10. The lubricant supply system of claim 1, in which saiddistributor element includes transfer slots and is shaped such that itseals, when lubricant is being supplied, both said partial areas,against one another until the attainment of a certain, pre-definedpressure in said first partial area and when said certain pressure isattained or exceeded, said pressure frees said transfer slots betweenthe first and the second partial areas.
 11. The lubricant supply systemaccording to claim 10, characterized in that the transfer slots have across-sectional area whose sum is much less than the sum of thecross-sectional areas of said lubricant supply conduits.
 12. Thelubricant supply system according to claim 11, characterized in that theratio between the sum of the cross-sectional areas of said transferslots to the sum of the cross-sectional areas of said lubricant supplyconduits can be freely established by one of the selection of thematerial of said distributor element and the fit between saiddistributor element and said distributor groove.
 13. The lubricantsupply system of claim 1, in which said distributor groove has anessentially constant cross section in radial direction.
 14. Thelubricant supply system of claim 1, in which said distributor groove isdivided in radial direction into two partial grooves, a first partialgroove which is the outer one in radial direction and a second partialgroove which is the inner one in radial direction; said inner partialgroove has, when arranged in said outer element, a larger cross sectionthan said outer partial groove, viewed in an axial section through saidouter element of the profile connection; and said distributor element isarranged in said inner partial groove.
 15. The lubricant supply systemaccording to claim 14, in which said distributor element rests on thecross-sectional transition in the inner partial groove.
 16. Thelubricant supply system according to claim 10, in which the width ofsaid distributor element is selected in such a manner that it has atleast the tolerance of one of a transition fit and a press fit, with thewidth of said distributor groove.
 17. The lubricant supply systemaccording to claim 10, in which said distributor element is designed tobe elastic in its circumferential direction and rigid over its width.18. The lubricant supply system of claim 10, in which said distributorelement comprises several layers.
 19. The lubricant supply systemaccording to claim 18, in which said layers are designed so that theycan move against each other in axial direction.
 20. The lubricant supplysystem of claim 10, in which said distributor element is constructed ofsemifinished material.
 21. The lubricant supply system according toclaim 10, in which said distributor element is a band.
 22. The lubricantsupply system according to claim 10, in which said distributor elementis formed by at least one part of a piston support ring.
 23. Thelubricant supply system according to claim 10, in which said distributorelement is formed by at least one part of a snap ring.
 24. The lubricantsupply system of claim 10, in which said distributor element is formedby at least one part of an O-ring.
 25. The lubricant supply system ofclaim 10, in which said distributor element is designed as an assemblyconsisting of a sealing element and a support element, said supportelement arranged on the inside, viewed in radial direction, when saiddistributor groove is arranged in said outer element, and when saiddistributor groove is arranged in said inner element said supportelement is arranged on the outside.
 26. The lubricant supply systemaccording to claim 25, in which said sealing element is elastic inradial direction.
 27. The lubricant supply system according to claim 25,in which said sealing element rests in a sealing manner on said innerwall of the distributor groove; at least a partial area of the innersurface of said sealing element, viewed in the assembled state in radialdirection, stands in contact with the outer surface of said supportelement; said sealing element comprises at least one passage crosssection which extends, viewed in the assembled state in radialdirection, from its outer surface to its inner surface; and the outersurface, viewed in the assembled state in radial direction, of thesupport element has a heightened roughness in comparison to the innersurface of the sealing element.
 28. The lubricant supply systemaccording to one claim 1, in which said distributor element is shaped insuch a manner and coupled to said distributor groove such that transfercross sections for lubricant are provided between said first partialarea and said second partial area in the area of profile gaps formed inthe profile base; and the sum of the area of said transfer crosssections is much smaller than the sum of the areas of the cross sectionsof said lubricant supply conduits.
 29. The lubricant supply systemaccording to claim 28, in which said transfer cross sections are formedby one of recesses and openings in said distributor element.
 30. Thelubricant supply system according to claim 28, in which said distributorgroove in said outer element is divided in radial direction into twopartial grooves, a first partial groove, the outer one in radialdirection, and a second partial groove, the inner one in radialdirection; said inner partial groove has a greater cross section, viewedin an axial section through the outer element of the profile connection,than said outer partial groove; and said transfer cross sections areformed by pocket-like recesses in the area of the transition from saidfirst to said second partial groove.
 31. The lubricant supply system ofclaim 28, in which said distributor element is rigid in one of thecircumferential direction and radial direction.
 32. Lubricant supplysystem (1) for a profile connection (2) of a shaft (3) and of a hub (4)with the ability to transfer torque between said shaft and hub and moveaxially and longitudinally; a first outer element of the profileconnection, shaft or hub, surrounds another, second, inner element ofthe profile connection, hub or shaft, at least partially incircumferential direction; at least one distributor groove (6) extendingover at least a part of the inner circumference (5) in circumferentialdirection is arranged in the area of the profile base (9) on the innercircumference (5) of the outer element (4) of the profile connection(2), said distributor groove located between said first outer elementand said second inner element; the distributor groove (6) is coupled toat least one lubricant supply conduit (8) extending to the outercircumference of the outer element (4) of the profile connection (2);characterized by the following features: a distributor element (12)extending over the length of the distributor groove (6) incircumferential direction is arranged in the distributor groove (6); thedistributor element (12) divides the distributor groove into a firstpartial area located radially outside and into a second partial arealocated radially inside (13.1, 13.2); and the distributor element (12)and the distributor groove (6) are designed and constructed in such amanner that they form in their cooperation a plurality of valvepositions between the first (13.1) and the second partial area (13.2) ofthe distributor groove (6).